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EP2021218B1 - Anhänger- und/oder vorderradbremsschaltventil, für traktor oder ähnliches fahrzeug - Google Patents

Anhänger- und/oder vorderradbremsschaltventil, für traktor oder ähnliches fahrzeug Download PDF

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Publication number
EP2021218B1
EP2021218B1 EP07725186.6A EP07725186A EP2021218B1 EP 2021218 B1 EP2021218 B1 EP 2021218B1 EP 07725186 A EP07725186 A EP 07725186A EP 2021218 B1 EP2021218 B1 EP 2021218B1
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EP
European Patent Office
Prior art keywords
valve
braking
disconnection
pressure
bore
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP07725186.6A
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English (en)
French (fr)
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EP2021218A1 (de
Inventor
Leonardo Cadeddu
Luigi Alberti
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
VHIT SpA
Original Assignee
VHIT SpA
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Priority claimed from ITTO20060353 external-priority patent/ITTO20060353A1/it
Priority claimed from IT000068A external-priority patent/ITTO20070068A1/it
Application filed by VHIT SpA filed Critical VHIT SpA
Publication of EP2021218A1 publication Critical patent/EP2021218A1/de
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Publication of EP2021218B1 publication Critical patent/EP2021218B1/de
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T11/00—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant
    • B60T11/10—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic
    • B60T11/16—Master control, e.g. master cylinders
    • B60T11/20—Tandem, side-by-side, or other multiple master cylinder units
    • B60T11/21—Tandem, side-by-side, or other multiple master cylinder units with two pedals operating on respective circuits, pressures therein being equalised when both pedals are operated together, e.g. for steering
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
    • B60T13/24—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being gaseous
    • B60T13/241—Differential pressure systems
    • B60T13/242—The control valve is provided as one unit with the servomotor cylinder
    • B60T13/245—Hydraulic command of the control valve, hydraulic transmission to the brake
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T17/00—Component parts, details, or accessories of power brake systems not covered by groups B60T8/00, B60T13/00 or B60T15/00, or presenting other characteristic features
    • B60T17/18—Safety devices; Monitoring
    • B60T17/22—Devices for monitoring or checking brake systems; Signal devices
    • B60T17/221—Procedure or apparatus for checking or keeping in a correct functioning condition of brake systems

Definitions

  • This invention concerns a valve intended to disconnect, in special circumstances, the braking of the front wheels and/or of the trailer, in a farm tractor or in a similar vehicle.
  • the hydraulic braking system includes two master cylinders controlled by two separate braking pedals, and each master cylinder controls the braking of one of the rear wheels of the vehicle.
  • This arrangement aims to allow a differential braking of the rear wheels, for example in order to facilitate the vehicle rotation for the U-turn during the cultivation of a field along adjacent lanes which are run in alternatively opposite directions.
  • a bilateral braking is effected by operating both the braking pedals, in general the system would not be balanced because the two separate braking circuits take up different oil quantities, and also the braking would then not be balanced.
  • a transfer channel is arranged for mutually communicating the two braking systems when both braking pedals are simultaneously operated. This balancing operation is effected by valves inserted on the pistons of the master cylinders, which valves are normally closed and are opened when the pistons run along a preestablished stroke.
  • the vehicles equipped with the above system may be devoid of brake devices acting on the front wheels and of brake devices in the trailer possibly dragged.
  • some systems are provided with brake devices also acting on the front wheels and/or with brake devices in the trailer, operated through a valve named "trailer brake valve", and in this case the systems comprise a hydraulic disconnecting valve intended to disconnect the braking of the front wheels and/or of the trailer in those cases in which only one braking pedal is operated, whereas, when both braking pedals are simultaneously operated, all the four wheels of the vehicle and/or the trailer wheels are braked.
  • the block diagram of such a braking system is represented in Figure 1
  • the corresponding hydraulic diagram is represented in Figure 2 . This system will be described with more details later on.
  • a disadvantage of this kind of braking systems is that the hydraulic disconnection valve has a complicated structure, to which follow high manufacturing and assembling costs as well as relatively easy breakdowns.
  • a typical example of the structure of this type of hydraulic disconnection valve is represented in Figure 3 , and its hydraulic diagram is represented in Figure 4 . This valve is described with more details later on.
  • the main object of the present invention is to substantially simplify the structure of the hydraulic valve intended for disconnecting the braking of the front wheels as well as of the trailer if present, in order to reduce the manufacturing and assembling costs and to render less probable the occurrence of breakdowns.
  • Another object of the invention is to further improve this hydraulic valve in order to simplify the operations for the cleaning of the hydraulic circuit when the same is filled with oil.
  • a valve for disconnection of the braking of the front wheels and/or of the trailer if present, through a trailer brake valve for a braking system of a vehicle having two pair of wheels all equipped with brake devices, or for a braking system of a vehicle having at least a pair of wheels equipped with brake devices and having a trailer brake valve
  • said vehicle having two master cylinders operating as pumps, each said master cylinder being operated by an own braking pedal, each said master cylinder directly controlling the braking of one rear wheel, and controlling the braking of the front wheels and/or of the trailer through a disconnection valve intended to disconnect the braking of the front wheels and of the trailer when only one of the braking pedals is operated
  • said disconnection valve comprising a body with a first and a second inlet connections intended to be connected each to one of the master cylinders, and comprising a delivery connection intended to be connected to a braking circuit of the front wheels, wherein: - said body has a first bore wherein
  • said interception valve is mounted along the displacement direction of said movable piston, and said movable piston has a pin directly acting onto said interception valve for opening the same.
  • said interception valve is a ball valve provided with a spring which thrusts the valve towards the closure position.
  • Said first bore of the valve body may be closed at an end thereof by a plug, against which rests said movable piston in its inoperative position, towards which it is pushed by a spring. Therefore this first bore is a blind bore.
  • said first bore of the valve body has several different diameters which decrease from an open end towards the opposite end, in order to allow inserting some packings by avoiding that these packings travel on holes or openings capable of damaging the packings at the time of the insertion thereof.
  • said plug is movable and it is provided with a clamping ring; between said movable plug and said clamping ring there is a spacing member suitable for keeping said movable piston in the position in which it opens the interception valve.
  • a spacing member suitable for keeping said movable piston in the position in which it opens the interception valve.
  • said spacing member is shaped in such a manner that it is automatically expelled when a braking pressure is applied to the disconnection valve.
  • a further development of the invention has the purpose of also solving another problem present in the vehicles of the mentioned kind.
  • the front brakes and the trailer brakes are underdimensioned.
  • the braking action is not optimal and, in certain conditions, as for example when traveling along an extensive slope, the rear brakes are excessively loaded and they undergo overheating.
  • a further object of this invention is to improve the disconnection valve in order that it allows an optimization of the ratio between the different pressures applied to the different brakes of the vehicle, so that no brake requires to be underdimensioned, and the braking action applied to the different wheels may be adapted to the layout of the own vehicle charges and also to the charges due to implements and tools mounted on the vehicle.
  • it is aimed to enable the disconnection valve to transmit to the front brakes of the vehicle, and to the brakes of the trailer if present, when the disconnection is not operated, a pressure proportionally reduced with respect to the pressure that is directly transmitted to the rear brakes of the vehicle.
  • Some devices are known that are intended to perform a proportional decrement of a pressure with the purpose of improve the braking actions, however the devices known to this aim are not suitable for being applied in the considered kind of vehicle, in which, when needed, should be effected the characteristic function of disconnection of the braking action.
  • the invention also concerns a valve for disconnecting the braking action, of the general kind above specified, which is characterized in that said movable piston has a second axial blind bore facing the first inlet connection, in that a tubular plunger is sealingly solid with the valve body and sealingly plunges in said second axial bore of the movable piston, in that said plunger defines at the bottom of said second axial blind bore a first chamber having the same cross section of said second bore and communicating through the passage of said tubular plunger with an external pressure, and in that said plunger defines in said first bore of the valve body an annular chamber communicating with said first inlet connection and having a cross section equal to the difference between the cross sections of said first and second bores; whereby the force applied to the movable piston by the pressure present in the first inlet connection is reduced, with respect to the product of said pressure present in the first inlet connection by the cross section of said first bore, according to a ratio resulting from the ratio between the cross sections of said first and second bores and from the ratio between the pressure present in said
  • Said external pressure may be the atmospheric pressure, and in this case said resulting ratio is invariable: it corresponds to the ratio between the cross sections of said first and second bores.
  • a push shaft passes through the passage of the tubular plunger and rests against said movable piston, and a mechanical thrust device is foreseen for applying to said push shaft an adjustable force and therefore for transmitting this adjustable force to the movable piston.
  • the mechanical thrust device may comprise a spring, whose compression may be adjusted by means of a control means such as a control wheel with a screw shaft.
  • the external pressure acting in said first chamber defined in said second bore is not the atmospheric pressure, but a pressure coming from an external adjustable pressure source.
  • the value of the external pressure is correspondingly modified the resulting ratio according to which is reduced the pressure coming from the second inlet connection for applying a pressure to the delivery connection. Therefore, also in this case it is possible to modify the behavior of the disconnection valve in order to adapt the same to the needs of a specific vehicle or to specific charge conditions of this vehicle.
  • the modification of the value of the external pressure may be effected by a manual control, or it may be automatically controlled by a system suitable for estimating the charge conditions of the vehicle and for adapting to the same the braking control effected by the disconnection valve.
  • Figure 1 shows the block diagram of such a system, of the kind wherein all the wheels are provided with braking devices
  • Figure 2 shows the hydraulic diagram of the same system.
  • the vehicle has four wheels: a left front wheel RAS with its own braking device, a right front wheel RAD with its own braking device, a left rear wheel RPS with its own braking device, and a right rear wheel RPD with its own braking device. It may be present a trailer RI, whose wheels are braked through a trailer brake valve VFR.
  • the braking of all these wheels is to be controlled by means of two braking pedals, a left pedal PS and a right pedal PD.
  • the left pedal PS is connected to a left master cylinder CMS, which receives oil from a reservoir S and, when the left pedal PS is operated, sends oil under pressure to the braking device of the left rear wheel RPS as well as to a disconnection valve VD intended to disconnect the braking of the front wheels and of the trailer if present.
  • the right left pedal PD is connected to a right master cylinder CMD, which receives oil from a reservoir S (in this case, the same reservoir which supplies the left master cylinder CMS) and, when the right pedal PD is operated, sends oil under pressure to the braking device of the right rear wheel RPD as well as to the disconnection valve VD intended to disconnect the braking of the front wheels and of the trailer if present.
  • the disconnection valve VD (to which the present invention specifically refers) has the purpose of disconnecting the braking of the front wheels RAS and RDS and/or of the trailer RI when only one of the pedals PS and PD is operated.
  • the two pedals PS and PD when singularly operated, allow to brake the only rear vehicle wheel which is situated on the same side as the operated pedal.
  • the simultaneous operation of both pedals PS and PD allows to brake all the vehicle wheels.
  • a balancing valve VB is interposed between the two master cylinders CMS and CMD and it equalizes the hydraulic pressures sent to the various wheels when both pedals PS and PD are simultaneously operated.
  • This balancing valve VB comprises component parts included in the master cylinders CMS and CMD.
  • a disconnection valve VD for disconnecting the braking of the front wheels and of the trailer if present comprises a body 1 with a bore wherein there are inserted two pistons 2 and 3 on which act the hydraulic pressures generated, respectively, by the master cylinder CMS and by the master cylinder CMD. These pressures are brought to the disconnection valve VD through respective inlet connections 4 and 5.
  • pistons 2 and 3 are inserted ball valves, respectively 6 and 7, which are normally closed by respective springs and can be opened by a spacing member 8.
  • the spacing member 8 is freely installed between the valves 6 and 7, and it is suitable for acting onto the valves when the two pistons 2 and 3 are displaced in mutual approach, thus opening the valves 6 and 7 (or at least one of them) for allowing the pressures coming from the inlet connections 4 and 5 to reach a delivery connection 9.
  • the delivery connection 9 supplies the braking devices of the front wheels and/or of the trailer RI if present, through the trailer brake valve VFR.
  • a spring 10 thrusts the pistons 2 and 3 to move mutually away, for their return to the rest positions when the pressures coming from the inlet connections 4 and 5 tend to zero.
  • a plug 11 closes the entrance of the bore wherein the pistons 2 and 3 are inserted.
  • Two cleaning valves 12 and 13 are put in communication with the inlet connections 4 and 5 for allowing the exhausting of the air present in the valve, at the time of its installation and then each time this exhaust is needed.
  • the operation of the represented valve is as follows.
  • an unilateral braking is effected by operating only one of the braking pedals PS and PD
  • only one of the two master cylinders CMS and CMD sends a pressure to the corresponding braking device of the rear wheel RPS or RPD, and also to the corresponding inlet connection 4 or 5 of the disconnection valve VD.
  • the corresponding piston 2 or 3 advances towards the other piston 3 or 2, and its ball valve 6 or 7, after having contacted the spacing member 8, pushes this spacing member 8 against the other ball valve 7 or 6.
  • the ball valve of the piston to which the pressure is applied is kept closed by this pressure, whereas the other ball valve, on which no pressure acts, is opened by the spacing member; but this opening gives no effect in the absence of a pressure. Therefore the pressure sent in this manner to the disconnection valve VD cannot reach the delivery connection 9, and the braking of the front wheels and/or of the trailer is not operated. As a consequence, in this situation only one rear wheel is braked.
  • both master cylinders CMS and CMD send a pressure to the corresponding braking device of the rear wheel RPS and RPD, and also to the corresponding inlet connection 4 and 5 of the disconnection valve VD.
  • both pistons 2 and 3 mutually approach, and at least one of the ball valves 6 and 7 (or both), having contacted the spacing member 8, is (are) opened by this spacing member against the action of their springs and of the pressures acting onto the ball valves.
  • At least one of the pressures sent to the disconnection valve VD reaches the delivery connection 9, and the braking of the front wheels (as well as of the trailer RI if present, through the trailer brake valve VFR) is activated. As a consequence, all the four wheels of the vehicle, and the wheels of the trailer if present, are braked.
  • a first embodiment of a disconnection valve VD according to this invention is represented in Figure 6 , and its hydraulic circuit is represented in Figure 5 .
  • the comparison between Figures 4 and 5 and between Figures 6 and 3 shows in evident manner how the disconnection valve embodied according to the invention is simplified with respect to the corresponding disconnection valve embodied according to the known technique.
  • the disconnection valve VD intended to disconnect the braking of the front wheels and/or of the trailer comprises a body 21 which has a first blind bore 38 wherein are inserted two pistons 22 and 23 onto which act the hydraulic pressures generated, respectively, by the master cylinders CNS and CMD, which enter the disconnection valve through inlet connections, respectively 24 and 25. Only in the piston 22 is inserted an interception ball valve 26, which is normally closed by a spring 27 resting against a clamping ring 35.
  • the interception ball valve 26 can be opened by a pin 28 carried by the piston 23, in order to allow the pressure coming from the inlet connection 24 to reach a delivery connection 29 which supplies the braking devices of the front wheels and/or the trailer brake valve VFR and, consequently, the braking devices of the trailer RI.
  • a spring 30 pushes piston 23 away from piston 22 for reverting piston 23 to its rest position. Piston 22 is blocked in an unmovable position by a clamping ring 34. A plug 31 closes the entrance of the first bore wherein the pistons 22 and 23 are inserted. A valve 33 for cleaning is put in communication with the inlet connection 25 for allowing exhausting of the air present in the valve and in the braking circuit, when the valve is installed and then each time such operation is needed.
  • piston 22, blocked in an unmovable position by the clamping ring 34, has an only structural function for carrying a seat against which acts the ball valve 26 and carrying the ring 35 against which rests ring 27 of the ball valve 26.
  • This arrangement is advantageous for the manufacture and assemblage of the valve, but it might be replaced by different arrangements wherein piston 22 may be omitted.
  • the seat for valve 26 might be carried directly by body 21 and a second plug could be provided, opposite plug 31, for closing a bore which in this case passes through the entire body 21.
  • the master cylinder CMD remains inactive, and the master cylinder CMS sends a pressure to the braking device of the corresponding rear wheel RPS and to the inlet connection 25 of the disconnection valve. This pressure displaces piston 23 against the action of spring 30.
  • the pin 28 of piston 23 acts against the ball valve 26 and opens this valve against the action of spring 35.
  • the inlet connection 24 does not receive any pressure, no pressure is transmitted to the delivery connection 29, and the braking of the front wheels and/or of the trailer is not activated. As a consequence, only the rear wheel RPS is braked.
  • the master cylinder CMS remains inactive, and the master cylinder CMD sends a pressure to the braking device of the corresponding rear wheel RPD and to the inlet connection 24 of the disconnection valve.
  • This pressure cannot displace the piston 23, which is blocked by the clamping ring 34.
  • the ball valve 34 remains closed, and no pressure is sent to the delivery connection 29, whereby also in this case the braking of the front wheels and/or of the trailer is not activated. As a consequence, only the rear wheel RPD is braked.
  • both the master cylinders CMS and CMD send pressures to the corresponding braking devices of the rear wheels RPS and RPD and to the corresponding inlet connections 24 and 25 of the disconnection valve. Then the movable piston 23 moves towards the fixed piston 22 and the ball valve 26 is opened by the pin 22 of piston 23, against the actions of spring 27 and of the pressure present in the inlet connection 24.
  • the action of the pressure present in the inlet connection 25 prevails on the action present in the inlet connection 24 because the pressure present in the inlet connection 25 is applied onto the section of piston 23, which is much larger than the section of the ball valve 26 which receives the action of the pressure present in the inlet connection 24.
  • the position thus assumed by the parts is represented in Figure 7 .
  • the pressure present in the inlet connection 24 reaches, through the open ball valve 26, the delivery connection 29, and the braking of the front wheels and/or of the trailer is activated. As a consequence, all the four wheels of the vehicle, and the trailer if present, are braked.
  • the first bore 38 is machined in the body 21 of the disconnection valve with three different diameters, which decrease from the entrance to the bottom.
  • the various packings intended to establish the seal of the component parts may be inserted from the bore entrance without sliding on holes or openings, and this reduces the possibility that the packings are damaged when mounting them.
  • the structure of the disconnection valve according to the invention is very simplified with respect to the known structure: one ball valve with its spring and the spacing member are suppressed, and the structure of the sole movable piston is very simple.
  • the manufacture and the assemblage are more simple and less costly, the causes of possible breakdowns are reduced and thus a great reliability is attained.
  • Figure 8 represent a second embodiment of a disconnection valve according to the invention, being an improvement of the first embodiment intended to render more easy the operation for exhausting air from the disconnection valve when the braking circuit is filled with oil.
  • a depression is applied to the circuit and the oil is introduced under pressure.
  • a spacing ring 37 of plastics which keeps in an advanced position the plug 31 and therefore also the movable piston 23 which rests against plug 31. Then the pin 28 of the movable piston 23 keeps permanently in open position the ball valve 26.
  • the disconnection valve is normally closed and it does not allow a depression, applied to the braking circuit of the rear wheels or to the reservoir, to be transmitted to the braking circuit of the front wheels.
  • a depression applied to the braking circuit of the rear wheels or to the reservoir
  • it is needed to apply a depression to two different points of the braking circuit namely a point communicating with the braking circuit of the rear wheels and another point communicating with the braking circuit of the front wheels.
  • the operation required for a braking circuit including a disconnection valve according to the known technique is therefore substantially more complicated that the operation required for a braking circuit including a disconnection valve according to the present invention.
  • the spacing ring 37 can be eliminated in order to allow the normal operation of the disconnection valve. It is of advantage that the spacing ring 37 is shaped, for example with a sloping external surface as shown by Figure 8 , in such a way that it is automatically expelled by the pressure established inside the disconnection valve on the occasion of the first braking operation.
  • the movable piston 23 has a second blind bore 39 whose entrance faces the first inlet connection 25, and a tubular plunger 40, sealingly solid with the body 21 of the disconnection valve, sealingly plunges in said second bore 39 of the movable piston 23.
  • the tubular plunger 40 is solid with the plug 31 which closes the first bore 38.
  • the tubular plunger 40 defines, at the bottom of the second blind bore 39, a first chamber 41 whose cross section is equal to the cross section of said second bore 39.
  • the first chamber 41 communicates, through the passage of said tubular plunger 40, with an external pressure P0.
  • tubular plunger 40 defines in said first bore 39 of body 21, between the movable piston 23 and the plug 31, a second chamber 42, which is annular and communicates with said first inlet connection 25.
  • the annular chamber 42 has a cross section S3 equal to the difference between the cross section S1 of the first bore 38 and the section S2 of the second bore 39.
  • both master cylinders CMS and CMD send pressures to the inlet connections 24 and 25, and the pressures sent to the two inlet connections are both equal to a value P1, thanks to the presence in the system of a balancing valve.
  • the force F1 applied to the movable piston by the pressure P1 present in the inlet connections 24 and 25 would be equal to the pressure P1 multiplied by the section S1 of the first bore 38.
  • the force F applied to the movable piston 23 is reduced, with respect to said force F1, according to a ratio R resulting from the ratio between the cross sections S1 and S2 of said first bore 38 and respectively of the second bore 39, and according to the ratio between the pressure P1 present in the inlet connections 24 and 25 and the external pressure P0.
  • the movable piston 23 takes a position in which said force F is equilibrated by the sum of the force applied by the return spring 30 and of the force F3 resulting by the pressure P3 present in the delivery connection 29 multiplied by the surface S1 of the cross section of the first bore 38.
  • the movable piston 23 opens the interception valve 26 only when said force F prevails on the force F3.
  • the pressure P3 transmitted by the disconnection valve VD to said delivery connection 29 is regulated on a value which is reduced, with respect to the pressure P1 present in said second inlet connection 24, according to said resulting ratio R.
  • This ratio R is therefore the regulation ratio of the disconnection valve VD.
  • the disconnection valve according to Figure 9 has an invariable regulation ratio R.
  • This regulation ratio may be adjusted to the need of a certain vehicle type and to the normal charge of the same, by adequately choosing the structural parameters of the disconnection valve, and in particular the surface S1 of the first bore 38 and the surface S2 of the second bore 39. Because the first chamber 41 communicates with the atmosphere, the pressure P0 therein present is invariable.
  • the described mechanical thrust device is only an example, and that this device may be designed in various manners, either for allowing a continuous adjustment of the operation conditions of the disconnection valve, or for allowing a stepwise adjustment, namely the selection among two or more preestablished operation conditions, which may correspond, for example, to the condition of discharged vehicle, to the condition of normal charge and to the condition of heavy charge.
  • a fifth embodiment of the invention is represented in Figure 11 .
  • the component parts already described with reference to Figure 9 are unchanged, but the passage traversing the tubular plunger 40 has a connection 48 intended to transmit to the first chamber 41 a pressure P4 coming from an external pressure source connected to the connection 48.
  • the force F applied to the movable piston 23 is reduced, with respect to the already cited force F1, according to a ratio RV resulting from the ratio between the cross sections S1 and S2 of said first bore 38 and respectively of the second bore 39, and according to the ratio between the pressure P1 present in said first inlet connections 25 and the adjustable external pressure P4, whereby the pressure P3 transmitted by the disconnection valve VD to said delivery connection 29 is reduced, with respect to the pressure P1 present in said second inlet connection 24, according to said resulting ratio RV.
  • the value of the external adjustable pressure P4 is also correspondingly modified the resulting ratio RV, which in this case is variable, according to which the pressure P1 coming from the second inlet connection 24 is reduced for its application to the delivery connection 29. Therefore, also in this case it is possible to modify the operation conditions of the disconnection valve VD, and in particular its regulation ratio RV, in order to adapt the same to a specific vehicle type or to specific charge condition of this vehicle.

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  • Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Control Valves For Brake Systems (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
  • Regulating Braking Force (AREA)

Claims (15)

  1. Ventil (VD), das dazu bestimmt ist, unter bestimmten Umständen die Bremsung der Vorderräder (RAS, RAD) und/oder die Bremsung des Anhängers (RI), wenn ein Bremssystem desselben über ein Bremsventil des Anhängers (VFR) angeschlossen ist, für ein Bremssystem für ein Fahrzeug mit zwei Paar Rädern, die alle mit Bremsvorrichtungen ausgestattet sind, bzw. für ein Fahrzeug mit mindestens einem Paar Rädern, die mit Bremsvorrichtungen ausgestattet sind und mit Bremsventil des Anhängers, abzuschalten, wobei das Bremssystem zwei Hauptbremszylinder (CMS, CMD) umfasst, die als Pumpen funktionieren und jeder Hauptbremszylinder von einem getrennten Bremspedal betätigt wird (PS, PD), das die Bremsung eines Hinterrads (RPS, RPD) direkt steuert und über ein Abschaltventil (VD) die Bremsung der Vorderräder und/oder die Bremsvorrichtung des Anhängers (RI) steuert, wenn dieser vorhanden ist, das dazu bestimmt ist, die Bremsung der Vorderräder und/oder des Anhängers in den Fällen abzuschalten, in denen nur eines der Bremspedale (PS, PD) betätigt wird, wobei dieses Abschaltventil einen Körper (21), eine erste Eingangsverbindung (25) und eine zweite Eingangsverbindung (24) umfasst, die dazu bestimmt sind, an die Hauptbremszylinder (CMS, CMD) angeschlossen zu werden und eine Durchflussverbindung (29) umfassen, die dazu bestimmt ist, an einen Bremskreis der Vorderräder (RAS, RAD) und/oder an das Bremsventil (VFR) des Anhängers angeschlossen zu werden, bei dem:
    - der genannte Körper (21) eine erste Bohrung (38) aufweist, in der ein beweglicher Kolben (23) montiert ist, auf den der auf die erste Eingangsverbindung (25) ausgeübte Druck wirkt;
    - der genannte Körper (21) ein Sperrventil (26) umfasst, das normalerweise geschlossen ist, das eine Verbindung zwischen der genannten zweiten Eingangsverbindung (24) und der genannten Ausgabeverbindung (29) sperrt;
    - und der genannte bewegliche Kolben (23) ein Organ (28) aufweist, das geeignet ist, das genannte Sperrventil (26) zu betätigen, um dieses zu öffnen, wenn der genannte bewegliche Kolben (23) durch den auf die erste Eingangsverbindung (25) wirkenden Druck verschoben wird und dadurch die Verbindung der genannten zweiten Eingangsverbindung (24) und der genannten Ausgangsverbindung (29) gestattet und damit das Wirken des in der genannten zweiten Eingangsverbindung (24) vorhandenen Drucks auf die genannte Durchflussverbindung (29).
    dadurch gekennzeichnet, dass sie einen zweiten Kolben (22) umfasst, der in die genannte erste Bohrung (38) des Körpers eingesetzt ist, wobei der genannte zweite Kolben (22) durch eine Haltevorrichtung fixiert wird und das genannte Sperrventil (26) trägt.
  2. Abschaltventil nach Anspruch 1, dadurch gekennzeichnet, dass das genannte Sperrventil (26) entlang der Richtung der Verschiebung des genannten beweglichen Kolbens (23) angeordnet ist und dass der genannte bewegliche Kolben (23) einen Stift (28) aufweist, der direkt auf das genannte Sperrventil (26) wirkt, um es zu öffnen.
  3. Abschaltventil nach Anspruch 1, dadurch gekennzeichnet, dass es sich bei dem genannten Sperrventil (26) um ein Kugelventil mit einer Feder (27) handelt, die das genannte Sperrventil (26) in die geschlossene Position bringt.
  4. Abschaltventil nach Anspruch 1, dadurch gekennzeichnet, dass die genannte erste Bohrung (38) des Körpers (21) des Ventils an einem Ende durch einen Verschluss (31) verschlossen wird, an dem der genannte bewegliche Kolben (23) in seiner Position der Inaktivität aufliegt, da der bewegliche Kolben (23) von einer Feder (30) zu dem genannten Verschluss (31) gedrückt wird.
  5. Abschaltventil nach Anspruch 1, dadurch gekennzeichnet, dass die genannte erste Bohrung (38) des Körpers (21) des Ventils mehrere unterschiedliche Durchmesser aufweist, die von einem offenen Ende desselben zu einem gegenüber liegenden Ende hin abnehmen.
  6. Abschaltventil nach Anspruch 5, dadurch gekennzeichnet, dass der genannte Verschluss (31) beweglich ist, dass er mit einem Befestigungsring (36) ausgestattet ist und dass zwischen dem genannten beweglichen Verschluss (31) und dem genannten Befestigungsring (36) eine Abstandsvorrichtung (37) angebracht ist, die geeignet ist, den genannten beweglichen Kolben (23) in der Position zu halten, in der dieser das Sperrventil öffnet, wobei die genannte Abstandsvorrichtung (27) eingesetzt wird, wenn der Bremskreis mit Öl gefüllt wird und dann entfernt wird, um die normale Funktionsweise des Abschaltventils zu gestatten.
  7. Abschaltventil nach Anspruch 6, dadurch gekennzeichnet, dass die genannte Abstandsvorrichtung (37) so beschaffen ist, dass sie automatisch ausgeworfen wird, wenn ein Bremsdruck auf das Abschaltventil wirkt.
  8. Abschaltventil der Bremsung nach Anspruch 1, dadurch gekennzeichnet, dass:
    - der genannte bewegliche Kolben (23) eine zweite axiale blinde Bohrung (39) aufweist, die zur ersten Eingangsverbindung (26) gerichtet ist,
    - ein Tauchrohr (40) hermetisch mit dem Körper (21) des Ventils verbunden ist und hermetisch in die genannte zweite axiale Bohrung (39) des beweglichen Kolbens (23) eintaucht,
    - das genannte Tauchrohr (40) am Boden der genannten zweiten axialen blinden Bohrung (39) eine erste Kammer (41) definiert, die den gleichen Querschnitt der genannten zweiten Bohrung (39) aufweist und über den Durchgang des genannten Tauchrohrs (40) mit einer externen Druckquelle (P0, P4) verbunden ist,
    - das genannte Tauchrohr (40) in der genannten ersten Bohrung (38) des Körpers (21) des Ventils eine ringförmige Kammer (42) definiert, die mit der ersten Eingangsverbindung (25) verbunden ist und einen Querschnitt aufweist, der dem Unterschied zwischen dem Querschnitt der genannten ersten Bohrung (38) und dem Querschnitt der genannten zweiten Bohrung (39) übereinstimmt;
    so dass die Kraft (F), die durch den Druck auf den beweglichen Kolben (23) wirkt, der in der genannten ersten Eingangsverbindung (25) vorliegt, im Vergleich zum Produkt (F1) des genannten Drucks (P1) verringert ist, der in der ersten Eingangsverbindung (25) für den Querschnitt der genannten ersten Bohrung (38) vorliegt, und zwar nach einem Verhältnis (R, RV), das sich aus dem Verhältnis zwischen den Querschnitten der genannten ersten Bohrung (38) und der genannten zweiten Bohrung (39) und dem Verhältnis zwischen dem Druck (P1), der in der genannten ersten Eingangsverbindung (25) vorliegt und dem genannten externen Druck (P0, P4) ergibt und der vom Abschaltventil an die genannte Durchflussverbindung (29) ist im Verhältnis zum Druck (P1), der im genannten zweiten Eingangsanschluss (24) vorliegt, nach dem genannten sich ergebenden Verhältnis (R, RV) verringert.
  9. Abschaltventil nach Anspruch 8, dadurch gekennzeichnet, dass eine Druckstange (43) durch den Durchgang des genannten Tauchrohrs (40) verläuft und am genannten beweglichen Kolben (23) aufliegt und eine mechanische Belastungsvorrichtung (44-47) so angebracht ist, dass eine einstellbare Kraft auf die genannte Druckstange (43) wirken und damit diese einstellbare Kraft auf den beweglichen Kolben (23) übertragen kann.
  10. Abschaltventil nach Anspruch 9, dadurch gekennzeichnet, dass die genannte mechanische Belastungsvorrichtung (44-47) eine Feder (44) umfasst, deren Druck über eine Steuerung wie ein Handrad (45) mit einer Schraubenwelle (46) reguliert werden kann.
  11. Abschaltventil nach Anspruch 8, dadurch gekennzeichnet, dass die externe Druckquelle (P0), die in der genannten ersten Kammer (41) wirkt, die in der genannten zweiten Bohrung (39) definiert wird, der atmosphärische Druck ist, so dass das sich ergebende Druckverhältnis unveränderlich ist und dem Verhältnis zwischen dem Querschnitt der genannten ersten Bohrung (38) und dem Querschnitt der genannten zweiten Bohrung (39) entspricht.
  12. Abschaltventil nach Anspruch 8, dadurch gekennzeichnet, dass die externe Druckquelle (P4), die in der genannten ersten, in der zweiten Bohrung (39) definierten Kammer (41) wirkt, eine einstellbare Druckquelle ist, so dass das genannte sich ergebende Einstellungsverhältnis (RV) veränderlich ist und an einen spezifischen Fahrzeugtyp und die Lastbedingungen desselben angepasst werden kann.
  13. Abschaltventil nach Anspruch 12, dadurch gekennzeichnet, dass der Wert des externen Drucks (P4) mittels manueller Steuerung reguliert wird.
  14. Abschaltventil nach Anspruch 12, dadurch gekennzeichnet, dass der Wert des genannten externen Drucks (P4) mittels einer automatischen Steuerung reguliert wird, die über ein System erzielt wird, das geeignet ist, die Lastbedingungen des Fahrzeugs zu beurteilen und diesen die Steuerung der Bremsung durch das Abschaltventil anzupassen.
  15. Abschaltventil nach Anspruch 9, dadurch gekennzeichnet, dass dieses in Kombination die Eigenschaften nach einem oder mehreren der Ansprüche 10 bis 14 umfasst.
EP07725186.6A 2006-05-16 2007-05-10 Anhänger- und/oder vorderradbremsschaltventil, für traktor oder ähnliches fahrzeug Active EP2021218B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
ITTO20060353 ITTO20060353A1 (it) 2006-05-16 2006-05-16 Valvola di disinserimento della frenatura anteriore e o del rimorchio, per un trattore agricolo o veicolo similre
IT000068A ITTO20070068A1 (it) 2007-01-31 2007-01-31 Valvola di disinserimento della frenatura anteriore e/o del rimorchio, per un trattore agricolo o veicolo similare
PCT/EP2007/004267 WO2007131758A1 (en) 2006-05-16 2007-05-10 A valve for disconnecting the front braking and/or the trailer braking, for a farm tractor or a similar vehicle

Publications (2)

Publication Number Publication Date
EP2021218A1 EP2021218A1 (de) 2009-02-11
EP2021218B1 true EP2021218B1 (de) 2014-07-16

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US (1) US8292051B2 (de)
EP (1) EP2021218B1 (de)
RU (1) RU2446067C2 (de)
WO (1) WO2007131758A1 (de)

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FR2964627B1 (fr) * 2010-09-14 2013-04-05 Poclain Hydraulics Ind Systeme de freinage ameliore
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ITTO20121065A1 (it) 2012-12-12 2014-06-13 Vhit Spa Sistema di frenatura idraulico per trattori agricoli e simili, e metodo di gestione di tale sistema
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ITUB20159195A1 (it) 2015-12-29 2017-06-29 Vhit Spa Dispositivo idraulico di comando della frenatura per veicoli agricoli e simili

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Also Published As

Publication number Publication date
RU2446067C2 (ru) 2012-03-27
US20090071778A1 (en) 2009-03-19
EP2021218A1 (de) 2009-02-11
WO2007131758A1 (en) 2007-11-22
US8292051B2 (en) 2012-10-23
RU2008149243A (ru) 2010-06-27

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